Magnetorheological fluid composition and vibration damping device using same

ABSTRACT

This vibration damping device ( 10 ) includes a magnetorheological fluid composition in a cylinder ( 12 ). The magnetorheological fluid composition includes magnetic particles; a dispersant having the magnetic particles dispersed therein; and a friction modifier. The friction modifier is an amine-based additive having a hydrocarbon chain having 14 to 22 carbon atoms, preferably an alkyl chain or an alkenyl chain. The content of the friction modifier is 0.1 to 5 mass %.

TECHNICAL FIELD

The present invention relates to a magnetorheological fluid compositionand a vibration damping device using the same.

BACKGROUND ART

As a vibration damping device, a variable damping force damper has beenknown which uses a magnetorheological fluid (MRF) composition to changeits apparent viscosity depending on the strength of a magnetic fieldapplied to the MRF composition. This vibration damping device dampsincoming vibration using flow resistance of the MRF composition which iscaused when a piston reciprocates in a cylinder filled with the MRFcomposition. This vibration damping device is capable of controlling thevibration damping force depending on the strength of the appliedmagnetic field.

Meanwhile, as the MRF composition, what is obtained by dispersingmagnetic particles into a dispersant is generally used. Thus, operatingpressure inside the cylinder is higher in the vibration damping deviceusing the MRF composition than in a vibration damping device using noMRF composition. Accordingly, the vibration damping device using the MRFcomposition involves a problem of an increase in frictional forcebetween frictionally slidable portions. In addition, in the vibrationdamping device using the MRF composition, the existence of magneticparticles of the MRF composition between the frictionally slidableportions makes the frictional force larger between the frictionallyslidable portions. Incidentally, an increase in the frictional forcebetween the frictionally slidable portions, for example, makes ridecomfort performance of a vehicle, to which this vibration damping deviceis applied, become worse, and makes the vibration damping device lessadaptable to a light-weight vehicle.

A vibration damping device has been disclosed in which: a piston rodconnected to a piston is slidably supported by an end portion of acylinder with a bearing; and this bearing is surrounded by a porousmember (see Patent Literature 1, for example).

This vibration damping device prevents the magnetic particles fromexisting between the frictionally slidable portion of the piston rod andthe frictionally slidable portion of the bearing by supplying onlyliquid components of the MRF composition, which are obtained byfiltering the magnetic particles from the MRF composition by the porousmember, to the interstice between the frictionally slidable portions.

In addition, a magnetic fluid formulation has been also known which isprepared with re-dispersability and low-temperature fluid behavior ofmagnetic particles taken into consideration (see Patent Literature 2,for example). However, no lubricant composition which contributes to anincrease in lubricity between the frictionally slidable portions, suchas a decrease in frictional force between the frictionally slidableportions while the vibration damping device is in operation, has beenknown yet.

CITATION LIST Patent Literatures

Patent Literature 1: Japanese Patent Application Publication No.2008-69858

Patent Literature 2: Japanese Patent Translation Publication No.2009-500816

SUMMARY OF INVENTION Technical Problem

The above-discussed vibration damping device (see Patent Literature 1,for example) requires seal members to be arranged in multiple locationsin order for the MRF composition (liquid components) to be supplied tothe interstice between the frictionally slidable portions via the porousmember alone. To put it specifically, a seal member is placed at leastbetween the inner wall of the cylinder and the porous member, as well asbetween the piston rod and the porous member, in addition to a sealmember being placed between the inner wall of the cylinder and thepiston rod. This vibration damping device also involves a problem of anincrease in the frictional force while the piston rod is reciprocatingrelative to the cylinder, since the multiple seal members are arrangedin the respective multiple locations around the piston rod.

What is more, the conventional vibration damping device involves aproblem of an increase in the number of component parts, a complexeddevice configuration, and a resultant increase in manufacturing costs.

With the above-discussed problems taken into consideration, an object ofthe present invention is to provide: a magnetorheological fluidcomposition which is capable of helping a vibration damping device tobasically reduce frictional force between a piston rod and a rod guidewhile the vibration damping device is in operation, without relying onsliding structures of the piston rod and the rod guide; and a vibrationdamping device using the magnetorheological fluid composition.

Solution to Problem

The inventors have found that use of a MRF composition blended with apredetermined chemical component leads to elimination of seal membersfrom a vibration damping device, and accordingly have arrived at thepresent invention.

The magnetorheological fluid composition according to the presentinvention, which has solved the above-discussed problems, includesmagnetic particles, a dispersant having the magnetic particles dispersedin the dispersant, and a friction modifier; the friction modifier is anamine-based additive having a hydrocarbon chain having 14 to 22 carbonatoms; and the content of the friction modifier is 0.1 to 5 mass %relative to a total amount of the magnetorheological fluid composition.

The vibration damping device according to the present invention, whichhas solved the above-discussed problems, includes: a cylinder filledwith the magnetorheological fluid composition according to claim 1; apiston rod inserted through the cylinder; a piston connected to thepiston rod and disposed in the cylinder to be slidable in an axialdirection; a first fluid chamber and a second fluid chamber defined inthe cylinder by the piston and each containing the magnetorheologicalfluid composition; a communication hole formed in the piston in such away that the first fluid chamber and the second fluid chambercommunicate with each other through the communication hole; and anelectromagnetic coil configured to apply a magnetic field to themagnetorheological fluid composition flowing in the communication hole.

Advantageous Effects of Invention

The present invention can provide: a magnetorheological fluidcomposition which is capable of helping a vibration damping device tobasically reduce frictional force while the vibration damping device isin operation, without relying on sliding structures; and a vibrationdamping device using the magnetorheological fluid composition. Thepresent invention further simplifies the configuration of the vibrationdamping device.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a cross-sectional view illustrating a schematic structure of avibration damping device according to an embodiment of the presentinvention.

FIG. 2 is a partially magnified cross-sectional view of a pistonillustrated in FIG. 1.

FIG. 3 is a partially magnified cross-sectional view of a rod guideillustrated in FIG. 1.

FIG. 4 is a partially magnified view illustrating an example of aconventional structure of the rod guide illustrated in FIG. 3.

FIG. 5 is a partially magnified view illustrating an example of aconventional improved structure of the rod guide illustrated in FIG. 3.

FIG. 6 is a graph comparatively showing a result of measurement test ofa friction coefficient of an example of the present invention and thoseof comparative examples.

FIG. 7 is a schematic diagram of a test apparatus which measuredfrictional forces in the example of the present invention and thecomparative examples.

FIG. 8 is a graph comparatively showing a result of a first measurementof frictional force of the example using the test apparatus illustratedin FIG. 7 and those of the comparative examples.

FIG. 9 is a graph comparatively showing results of a second measurementof frictional forces obtained by sliding a piston rod over the rod guidewith loads (F) of 50 N, 150 N and 300 N in the example using the testapparatus illustrated in FIG. 7 and those in the comparative examples.

DESCRIPTION OF EMBODIMENTS

Descriptions will be hereinbelow provided for a magnetorheological fluidcomposition according to an embodiment of the present invention, and avibration damping device using the same. The descriptions will startwith an overall configuration of the vibration damping device, and go onto the magnetorheological fluid composition to be used for the vibrationdamping device.

<Overall Configuration of Vibration Damping Device>

FIG. 1 is a cross-sectional view illustrating a schematic structure ofthe vibration damping device 10 according to the embodiment of thepresent invention.

The vibration damping device 10 is a mono tube-type (de Carbon-type)variable damping force vehicular damper, and is configured to controlvibration damping force depending on magnitude of incoming vibrationfrom wheels.

The vibration damping device 10 includes: a tube-shaped cylinder 12filled with a magnetorheological fluid (MRF) composition, which will bedescribed in detail later; a piston rod 13 slidable inside the cylinder12 in an axial direction (longitudinal direction) of the cylinder 12; apiston 16 which is attached to the distal end of the piston rod 13, andwhich divides the inside of the cylinder 12 into a first fluid chamber14 and a second fluid chamber 15; and a free piston 18 which divides theinside of the cylinder 12 into the second fluid chamber 15 and ahigh-pressure gas chamber 17. It should be noted that the piston 16corresponds to a “piston” in the scope of claims.

One end of the cylinder 12 is provided with a rod guide 19 which closesthe opening of the cylinder 12. The rod guide 19 has a substantiallycylindrical shape.

The piston rod 13 is inserted through and supported by a center hole ofthe rod guide 19.

The outer circumferential surface of the piston rod 13 (a piston rod13-side frictionally slidable portion) slides over the innercircumferential surface of the rod guide 19 (a rod guide 19-sidefrictionally slidable portion).

The rod guide 19 includes an oil seal 26 for preventing themagnetorheological fluid composition from leaking to the outside.Detailed descriptions will be provided for the structure of the rodguide 19 later.

The other end of the cylinder 12 is usually provided with an eyepiece 12a. For example, in a case where this vibration damping device 10 is usedas a vehicular suspension, a bolt (not illustrated) is inserted in theeyepiece 12 a, and the bolt is connected to a trailing arm, a wheel-sidemember.

Furthermore, the end portion (the end portion on the left side inFIG. 1) of the piston rod 13 is connected to a damper base, a vehiclebody-side member (above a wheel house), with the assistance of a dampermount. While the vehicle is running, the outer circumferential surfaceof the piston 16 and the outer circumferential surface of the freepiston 18 slide over the inner circumferential surface of the cylinder12.

FIG. 2 shows a partially magnified cross-sectional view of the piston 16illustrated in FIG. 1.

The piston 16 includes: a communication hole 21 through which the firstfluid chamber 14 and the second fluid chamber 15 communicate with eachother; and an electromagnetic coil 22 for applying a magnetic field tothe magnetorheological fluid composition which flows in thecommunication hole 21. An electric current is supplied to theelectromagnetic coil 22 through a power supply line 23.

The power supply line 23 runs inside the piston rod 13, is drawn out ofthe piston rod 13, and is connected to a predetermined control powersupply (not illustrated).

When the electric current is supplied to the electromagnetic coil 22from the control power supply through the power supply line 23, themagnetic field is applied to the magnetorheological fluid composition inthe communication hole 21. On this occasion, except for themagnetorheological fluid composition flowing in the communication hole21, the magnetorheological fluid composition is stationary, and magneticparticles included in the stationary magnetorheological fluidcomposition align themselves along the lines of magnetic flux to formclusters. On the other hand, the magnetorheological fluid composition inthe communication hole 21 flows therein in a way that hinders theformation of clusters, and increases its apparent viscosity.

The vibration damping device 10 of the embodiment detects the magnitude,amplitude and velocity of incoming vibration using a predeterminedsensor, and based on a detection signal, controls electric power to besupplied to the electromagnetic coil 22. Thereby, the vibration dampingdevice 10 increases the apparent viscosity of the magnetorheologicalfluid composition in response to the magnitude of the incomingvibration, and thus controls damping force. In FIG. 2, reference sign 12denotes the cylinder.

FIG. 3 shows a partially magnified cross-sectional view of the rod guide19 illustrated in FIG. 1.

The rod guide 19 includes: a substantially cylindrical substrate part 31which is fitted in a one end-side portion of the cylinder 12, andthrough which the piston rod 13 is inserted; a substantially cylindricalguide metal 32 which is disposed on the inner circumference of thesubstrate part 31, and which slidably supports the piston rod 13; an oilseal 26 which is disposed on the inner circumference of the substratepart 31, and which fluid-tightly seals the interstice between thesubstrate part and the piston rod 13 while slidably supporting thepiston rod 13.

The substrate part 31 of the embodiment is made, for example, ofiron-based metal material such as steel material, or non-magnetic metalmaterial such as aluminum, aluminum alloy or stainless steel. Thesubstrate part 31 is press-fitted into the opening of the cylinder 12,and fluid-tightly seals the one end of the cylinder 12. How to attachthe substrate part 31 to the cylinder 12 is not limited topress-fitting. Screwing, welding or other mode can be employed as theattaching mode.

The inner circumference of the substrate part 31 includes: asmall-diameter portion 35 which is formed near the one end of thecylinder 12, and whose inner diameter is large enough for thesmall-diameter portion 35 to slidably touch the outer circumferentialsurface of the piston rod 13; a large-diameter portion 36 whose innerdiameter is larger than that of the small-diameter portion 35; and anoil seal placement portion 37 which is formed between the small-diameterportion 35 and the large-diameter portion 36, and whose inner diameteris larger than that of the large-diameter portion 36.

The guide metal 32 is made, for example, of a metal material such assteel, aluminum alloy, copper alloy, stainless steel. The guide metal 32is placed on the large-diameter portion 36.

The inner circumferential surface of the metal guide 32 of theembodiment is coated with fluororesin coating, or powder sinteredcompact of copper, tin, nickel or the like. Incidentally, the outercircumferential surface of the piston rod 13 of the embodiment ishard-plated or hard-coated with nickel, chromium, amorphous carbon(diamond-like carbon), ceramics, or the like. This configuration makesfrictional resistant small between the contact surfaces (frictionallyslidable portions) of the piston rod 13 and the guide metal 32.

The oil seal 26 of the embodiment is made of a polymer elastomer such asurethane resin, fluororesin and silicon resin, or a rubber-basedmaterial such as nitrile butyl rubber.

The oil seal 26 is provided on the oil seal placement portion 37 in thesubstrate part 31. The oil seal 26 is in press contact with the pistonrod 13 and the substrate part 31, and thereby prevents themagnetorheological fluid composition from leaking to the outside.

It should be noted that: in the conventional vibration damping deviceusing the conventional magnetorheological fluid composition, another oilseal is placed between the guide metal 32 and the first fluid chamber14; and in contrast, the embodiment eliminates such an oil seal. Thereason why this oil seal can be eliminated from the embodiment is thatthe embodiment uses the below-described magnetorheological fluidcomposition of the present invention, as described in detail later.

<Magnetorheological Fluid Composition>

The magnetorheological fluid composition contains: magnetic particles; adispersant for dispersing the magnetic particles; and a frictionmodifier.

(Magnetic Particles)

Citable examples of the material of the magnetic particles include iron,iron nitride, iron carbide, carbonyl iron, chromium dioxide, low carbonsteel, nickel and cobalt. Otherwise, usable as the material of themagnetic particles are, for example, iron alloys such asaluminum-containing iron alloy, silicon-containing iron alloy,cobalt-containing iron ally, nickel-containing iron alloy,vanadium-containing iron alloy, molybdenum-containing iron alloy,chromium-containing iron alloy, tungsten-containing iron alloy,manganese-containing iron alloy and copper-containing iron alloy.Alternatively, usable as the material of the magnetic particles are, forexample, paramagnetic, superparamagnetic or ferromagnetic chemicalcompound particles of gadolinium or an organic gadolinium derivative, orparticles of their mixture.

It should be noted that magnetic particles of soft magnetic material arepreferable since they are magnetized when a magnetic field is applied tothem, and are substantially demagnetized when no magnetic field isapplied to them.

As such a material of the magnetic particles, particularly carbonyl ironis preferable since carbonyl iron is a soft magnetic material with a lowmagnetic coercivity and a high magnetic permeability.

When obtained by the Brunauer-Emmett-Teller (BET) method, the averageparticle diameter of the magnetic particles may be set at approximately50 nm to 50 μm. When used as the magnetorheological fluid, the magneticparticles has an average particle diameter of, preferably 1 μm to 10 μm,more preferably 2 μm to 9 μm, and most preferably 3 μm to 8 μm.

Furthermore, the surfaces of the magnetic particles may be modified forthe purpose of enhancing the affinity of the particles for thedispersant and the dispersibility of the particles. The surfacemodification can be achieved, for example, by applying a silane couplingagent to the surfaces of the magnetic particles.

(Dispersant)

Any liquid capable of dispersing the magnetic particles may be used asthe dispersant. Particularly, mineral oil and synthetic oil ispreferable. Mineral or synthetic oil to be generally used as base oilfor engine lubricating oil, driving oil, shock absorber fluid ormachining oil may be used as the dispersant. Although no specificrestriction is imposed on the viscosity coefficient of the dispersant,the viscosity coefficient at 40° C. is preferably in a range in 0.01 to0.3 Pa·s, more preferably in a range in 0.02 to 0.2 Pa·s, and mostpreferably in a range in 0.03 to 0.15. Pa·s.

Furthermore, although no specific restriction is imposed on the pourpoint as an index of the low-temperature fluidity of the mineral oil andthe synthetic oil, the pour point is preferably −20° C. or less, morepreferably −30° C. or less, and most preferably −40° C. or less, becausethe mineral oil and the synthetic oil needs to be usable at lowtemperature.

Citable examples of the mineral oil include: distillates obtained byatmospherically distilling paraffinic crude oil, intermediate crude oiland naphthenic crude oil; distillates obtained by vacuum-distillingresidual oil which remains after the atmospheric distillation; andrefined oils, such as solvent-refined oil, hydrogenated refined oil,dewaxed oil and clay-treated oil, obtained by refining these distillatesusing conventional methods.

Citable examples of the synthetic oil includes poly α-olefin, α-olefincopolymer, polybutene, alkylbenzene, polyol ester, dibasic acid ester,olyoxyalkylene glycol, polyoxyalkylene glycol ester, polyoxyalkyleneglycol ether, and silicone oil.

The above-cited dispersants can be used singly or in combination of twoor more.

(Friction Modifier)

The friction modifier is an amine-based additive.

Citable examples of the amine-based additive include saturated aliphaticamine, unsaturated aliphatic amine, or aromatic amine. The amine-basedadditive may be primary amine, secondary amine, or tertiary amine. Theprimary amine is preferable. The more preferable is primary aromaticamine having a hydrocarbon chain having 14 to 22 carbon atoms. Thehydrocarbon chain is preferably an alkyl chain or an alkenyl chain. Theparticularly preferable primary aromatic amine has an alkenyl chain. Thealkenyl chain has, preferably 15 to 21 carbon atoms, and more preferably16 to 20 carbon atoms. It should be noted that: oily effect can beexpected from a hydrocarbon chain having 14 or more carbon atoms; andeffect of adsorption on the friction surface can be expected from ahydrocarbon chain having 22 or less carbon atoms.

Herein, saturated aliphatic primary amine and unsaturated aliphaticprimary amine are particularly preferable. Examples of the saturatedaliphatic primary amine include decylamine, undecylamine, dodecylamine,tridecylamine, tetradecylamine, pentadecylamine, cetylamine,stearylamine, palmitylamine. Examples of the unsaturated aliphaticprimary amine include oleylamine.

The content of the magnetic particles is 60 to 85 mass %.

In addition, the content of the dispersant inclusive of the frictionmodifier (additive) in the magnetorheological fluid composition is 15 to40 mass %, more preferably 20 to 35 mass %, and most preferably 20 to 25mass %. Viscous characteristic effect (during application of magneticload) can be expected when the content of the magnetic particles is 60mass % or greater. Dispersibility effect can be expected when thecontent of the magnetic particles is 85 mass % or less.

Furthermore, the content of the friction modifier (additive) in themagnetorheological fluid composition is 0.1 to 5 mass %, more preferably0.4 to 3 mass %, and most preferably 0.7 to 1.5 mass %. Oily effect canbe expected when the content of the friction modifier is 0.1 mass % orgreater. Effect of adsorption on the friction surface can be expectedwhen the content of the friction modifier is 5 mass % or less.

Moreover, an ester solvent such as sebacic acid bis (2-ethylhexyl), aviscosity modifier such as organophilic bentonite, a solid lubricantsuch as molybdenum disulfide, and other additives having functions suchas dispersibility, heat resistance, oxidation resistance, corrosionresistance and defoaming property may be also added to themagnetorheological fluid composition.

The magnetorheological fluid composition is prepared by: blending themagnetic particles, the dispersant, and the friction modifier (additive)in their respective contents; and mixing them together.

The vibration damping device 10 of the embodiment having theabove-discussed structure is manufactured by filling the cylinder 12with the magnetorheological fluid composition before or after the piston16 is installed in the cylinder 12.

Next, descriptions will be provided for working and effects which isobtained from the vibration damping device 10 of the embodiment.

The magnetorheological fluid composition used in the vibration dampingdevice 10 is capable of further reducing frictional force between thefrictionally slidable portions even in the case where themagnetorheological fluid composition inclusive of the magnetic particlesexists between the frictionally slidable portions, since themagnetorheological fluid composition contains the above-discussedfriction modifier. One may consider that the reason for the reduction infrictional force is that part of the magnetorheological fluidcomposition containing the friction modifier forms a low-frictionboundary film between the frictionally slidable portions.

Furthermore, the vibration damping device 10 using thismagnetorheological fluid composition is capable of reducing frictionalforce to a large extent while the vibration damping device 10 is inoperation, and decreasing dependency of the frictional force on lateralforce load.

Moreover, the vibration damping device 10 reduces the frictional forceusing the magnetorheological fluid composition containing the frictionmodifier, and the vibration damping device 10 is capable of reducingfrictional force between each two component parts which slide over eachother in the magnetorheological fluid composition. To put itspecifically, the conventional vibration damping device (see PatentLiterature 1, for example) reduces frictional force between the limitedparts of the frictionally slidable portions defined by the porousmember. In contrast to this, the vibration damping device 10 of theembodiment is capable of reducing frictional force in all thefrictionally slidable portions which the magnetorheological fluidcomposition spreads, although its configuration is simpler than that ofthe conventional vibration damping device, and although it wouldotherwise need to rely on the internal structure.

Moreover, the vibration damping device 10 of the embodiment makes itpossible to decrease the number of oil seals 26 (seal members) placedbetween the piston rod 13 and the rod guide 19, and is accordinglycapable of reducing the frictional force much more.

Although the foregoing descriptions have been provided for theembodiment of the present invention, the present invention is notlimited to the embodiment, and can be carried out in various modes.

FIG. 4 is a partially magnified view illustrating an example of aconventional structure of the rod guide 19 illustrated in FIG. 3.

In the embodiment, as illustrated in FIG. 3, the oil seal 26 between thesubstrate part 31 and the piston rod 13 in the rod guide 19 is placedcloser to an opening end portion of the cylinder 12 (to the left in FIG.3) than the guide metal 32 is. In other words, the guide metal 32 in therod guide 19 of the embodiment is placed within the first fluid chamber14, and is thus capable of sliding under a lubrication environment usingthe magnetorheological fluid composition of the embodiment.

In contrast to this, as illustrated in FIG. 4, in the rod guide 19 asthe conventional structure example, the oil seal 26 between thesubstrate part 31 and the piston rod 13 is placed closer to the firstfluid chamber 14 (to the right in FIG. 4) than the metal guide 32 is.

The conventional magnetorheological fluid composition has higherfrictional force, and forms no boundary film between the frictionallyslidable portions unlike the friction modifier of the embodiment. Thus,the magnetic particles contained therein are highly aggressive.Accordingly, in the rod guide 19 as the conventional structure example,it is necessary to avoid existence of the magnetic particles between thefrictionally slidable portions of the guide metal 32 and the piston rod13.

The guide metal 32 in the rod guide 19 as the conventional structureexample undergoes dry friction with no magnetorheological fluidcomposition. The oil seal 26 and the piston 16 disposed at the distalend of the piston rod 13, however, can be lubricated in the environmentusing the magnetorheological fluid composition of the embodiment. Thisenables even the conventional structure as illustrated in FIG. 4 toreduce frictional force in the vibration damping device 10, andaccordingly to use the magnetorheological fluid composition of theembodiment effectively, although the performance is not so high as thatof the embodiment.

FIG. 5 is a partially magnified view illustrating an example of aconventional improved structure of the rod guide 19 illustrated in FIG.4.

As illustrated in FIG. 5, in the rod guide 19 as the conventionalimproved structure example, a guide metal holder 33 made of asubstantially cylindrical body of a porous member is disposedsurrounding the guide metal 32 through which the piston rod 13 isinserted. This guide metal holder 33 is fitted into the substrate part31 of the substantially cylindrical rod guide 19. Reference sign 26denotes oil seals. In the two axial end portions of the guide metalholder 33, respectively, the oil seals 26 seal the interstice betweenthe guide metal holder 33 and the piston rod 13. Reference 12 denotesthe cylinder. Reference 14 denotes the first fluid chamber.

In the vibration damping device 10 including the rod guide 19 as theconventional improved structure example, only the liquid components ofthe MRF composition, which are obtained by the filtering of the magneticparticles from the MRF composition by the guide metal holder 33 of theporous member, is supplied to the interstice between the piston rod 13and the guide metal holder 33 in which the guide metal 32 is placed.

Thus, the vibration damping device 10 including the rod guide 19 withthe conventional improved structure prevents the magnetic particles fromexisting between the frictionally slidable portions, and accordinglymaintains the lubricity between the frictionally slidable portions usingthe liquid components of the MRF composition.

The multiple oil seals 26, however, need to be arranged in order toisolate the guide metal holder 33. This inevitably makes frictionalforce due to the oil seals 26 higher. In the vibration damping device 10provided with the rod guide 19 of the conventional improved structure,however, the liquid components of the MRF composition is supplied to theinterstice between the frictionally slidable portions of the guide metal32 and the piston rod 13 via the guide metal holder 33 of the porousmember. In the vibration damping device 10 provided with the rod guide19 of the conventional improved structure, supplying the frictionmodification additive of the embodiment to the interstice between thefrictionally slidable portions of the guide metal 32 and the piston rod13 is capable of reducing friction although the performance is not asgood as that of the embodiment.

Moreover, like in the conventional structure example illustrated in FIG.4, the oil seals 26, and the piston 16 disposed at the distal end of thepiston rod 13 are lubricated under the environment using the MRFcomposition of the embodiment. Accordingly, the piston 6 makes thefrictional force reduced in the vibration damping device 10, and themagnetorheological fluid composition of the embodiment is effectivelyused in the vibration damping device 10.

The foregoing descriptions have been provided for how effective themagnetorheological fluid composition of the present invention is inembodiments other than the above-discussed embodiment. The presentinvention is not limited to the above-discussed embodiment, and may becarried out in other various embodiments.

In addition, although the foregoing embodiment has discussed thevibration damping device 10 to be used in vehicles, the vibrationdamping device 10 is limited to this use. The vibration damping device10 is also applicable to anti-vibration devices in other fields such asthe home appliance field and the civil engineering/constructionequipment field.

Example

Descriptions will be hereinbelow provided for Example to be used toexamine the working and effects of the present invention, andComparative Examples 1 to 4. It should be noted that: the presentinvention is not limited to the following example; and the presentinvention can be carried out by being arbitrarily modified within ascope not departing from the gist and spirit of the present invention.

<Preparation of Magnetorheological Fluid Compositions>

First of all, standard MRF (MRF 126-CD, produced by Lord Corporation),generally commercially available as MRF, was used as the base materialof magnetorheological fluid compositions. Incidentally, the standard MRFcontains magnetic particles and a dispersant for dispersing the magneticparticles.

Next, the magnetorheological fluid compositions to be used for Exampleand Comparative Examples 1 to 4 were prepared by mixing the basematerial and the friction modifier in accordance with the contents (mass%) shown in Table 1.

TABLE 1 Compar- Compar- Compar- Compar- ative ative ative ative Ex-Example 1 Example 2 Example 3 Example 4 ample MRF 100 99 99 99 99(standard · base) (mass %) Phosphorus- 1 based Additive (mass %) FattyAcid 1 (mass %) Amino 1 Acid-based Additive (mass %) Amine-based 1Additive (mass %)

The amine-based additive as the friction modifier in Example wasmonooleylamine (9-octadecene-1-amine) having a hydrocarbon chain having18 carbon atoms.

The magnetorheological fluid composition in Comparative Example 1 wasthe base material itself.

The phosphorus-based additive in Comparative Example 2 was oleyl acidphosphate.

The fatty acid in Comparative Example 3 was stearic acid.

The amino acid-based additive in Comparative Example 4 was N-oleylsarcosine.

<Measurement of Friction Coefficients>

Each coefficient of friction between the frictionally slidable part ofthe oil seal 26 (see FIG. 3) and the frictionally slidable part of thepiston rod 13 (see FIG. 3) was measured on the assumption that the oilseal 26 was made of urethane resin and the surface of the piston rod 13was plated with hard chromium.

The measurement test was conducted by: applying the preparedmagnetorheological fluid composition onto a metal plate whose surfacewas plated with hard chromium; and reciprocally sliding a urethaneresin-made block body over the metal plate while applying a load of 19.6N (2.00 kgf) to the block body. The measurement test temperature was 60°C.; the sliding stroke was 10 mm; and the sliding speed was 0.5 mm/s.

Table 2 and FIG. 6 show results of measuring the friction coefficients.

TABLE 2 Compar- Compar- Compar- Compar- ative ative ative ative Ex-Example 1 Example 2 Example 3 Example 4 ample Friction 0.119 0.033 0.0420.055 0.023 Coefficient

FIG. 6 is a graph comparatively showing a result of measurement test ofthe friction coefficient of Example of the present invention and resultsof measurement test of the friction coefficients of Comparative Examples1 to 4.

<Measurement of Frictional Forces>

Each frictional force between the frictionally slidable part of thecylindrical guide metal 32 (see FIG. 3) and the frictionally slidablepart of the piston rod 13 was measured on the assumption that the innercircumferential surface of the guide metal 32 is coated withpolytetrafluoroethylene (PTFE) and the surface of the piston rod 13 wasplated with hard chromium.

FIG. 7 is a schematic diagram of a test apparatus which measuredfrictional forces.

The test apparatus 40 included: an oil bath 42 filled with amagnetorheological fluid composition 41; and the rod guide 19 which wasplaced inside the oil bath 42, and to which the guide metal 32 wasattached.

In FIG. 7, reference sign 13 denotes the piston rod which was insertedthrough the guide rod 19, and which was slidably supported by the guidemetal 32. Reference sign 26 denotes the oil seals which fluid-tightlysealed the interstice between the oil bath 42 and the piston rod 13.

This test apparatus 40 was designed to apply load F to the intersticebetween the guide metal 32 and the piston rod 13 via the rod guide 19while reciprocating the piston rod 13 in the axial directions D.

First of all, in this measurement test, frictional forces were measuredwhich were produced by sliding the piston rod 13 for four hours underconditions including a sliding speed of 25 mm/s, a sliding stroke of 10mm and a load (F) of 150 N. Incidentally, the measurement test wasconducted with the frictionally slidable parts completely soaked in themagnetorheological fluid composition. Table 3 and FIG. 8 show results ofthis first measurement.

TABLE 3 Compar- Compar- Compar- Compar- ative ative ative ative Ex-Example 1 Example 2 Example 3 Example 4 ample Frictional 51.5 40.3 45.146.6 23.7 Force [N]

FIG. 8 is a graph comparatively showing a result of the firstmeasurement of the frictional force of Example and those of ComparativeExamples 1 to 4.

After this measurement test, frictional forces were measured which wereproduced by sliding the piston rod 13 under conditions including asliding speed of 0.15 mm/s, a sliding stroke of 5 mm, as well as loads(F) of 50 N, 150 N and 300 N. Table 4 and FIG. 9 show results of thissecond measurement.

TABLE 4 Compar- Compar- Compar- Compar- Frictional ative ative ativeative Force [N] Example 1 Example 2 Example 3 Example 4 Example Load 5028.8 24.8 25.1 27.2 15.1 [N] 150 51.5 40.3 45.1 46.6 23.7 300 96.3 62.676.4 77.3 38.5

FIG. 9 is a graph showing results of the second measurement offrictional forces obtained by sliding the piston rod with loads (F) of50 N, 150 N and 300 N in Example and those in Comparative Examples 1 to4.

<Results of Evaluation of Magnetorheological Fluid Compositions>

As shown in FIG. 6, the friction coefficients obtained by the frictionbetween the oil seal 26 (see FIG. 3) made of urethane resin and thepiston rod 13 (see FIG. 13) plated with hard chromium using themagnetorheological fluid compositions of Example and ComparativeExamples 2 to 4 were less than half of that obtained using themagnetorheological fluid composition of Comparative Example 1 (the basematerial). Particularly, the friction coefficient obtained using themagnetorheological fluid composition of Example was approximate onesixth of that obtained using the magnetorheological fluid composition ofComparative Example 1 (the base material).

As shown in FIG. 8, the frictional force of the piston rod 13 platedwith hard chromium against the guide metal 32 (see FIG. 3) coated withpolytetrafluoroethylene (PTFE) in use of the magnetorheological fluidcomposition of Example was approximately a half of those in use of themagnetorheological fluid compositions of Comparative Examples 1 to 4.

As shown in FIG. 9, the frictional forces of the piston rod 13 platedwith hard chromium, which were obtained by sliding the piston rod 13over the guide metal 32 (see FIG. 3) coated with polytetrafluoroethylene(PTFE) with loads (F) of 50 N, 150 N and 300 N in use of themagnetorheological fluid composition of Example, were extremely smallerthan those obtained in use of the magnetorheological fluid compositionsof Comparative Examples 1 to 4. The rate (gradient) of increase infrictional force with respect to each load (N) in use of themagnetorheological fluid composition of Example was the smallest amongall the measured rates.

REFERENCE SIGNS LIST

-   10 vibration damping device-   12 cylinder-   12 a eyepiece-   13 piston rod-   14 first fluid chamber-   15 second fluid chamber-   16 piston-   17 high-pressure gas chamber-   18 free piston-   19 rod guide-   21 communication hole-   22 electromagnetic coil-   23 power supply line-   26 oil seal-   31 substrate part-   32 guide metal-   33 guide metal holder-   35 small-diameter portion-   36 large-diameter portion-   37 oil seal placement portion

The invention claimed is:
 1. A magnetorheological fluid composition comprising: magnetic particles; a dispersant having the magnetic particles dispersed in the dispersant; and a friction modifier, wherein the friction modifier is an amine-based additive having a hydrocarbon chain having 14 to 22 carbon atoms, wherein the content of the friction modifier is 0.1 to 5 mass % relative to a total amount of the magnetorheological fluid composition.
 2. A vibration damping device comprising: a cylinder filled with the magnetorheological fluid composition according to claim 1; a piston rod inserted through the cylinder; a piston connected to the piston rod and disposed in the cylinder to be slidable in an axial direction; a first fluid chamber and a second fluid chamber defined in the cylinder by the piston and each containing the magnetorheological fluid composition; a communication hole formed in the piston in such a way that the first fluid chamber and the second fluid chamber communicate with each other through the communication hole; and an electromagnetic coil configured to apply a magnetic field to the magnetorheological fluid composition flowing in the communication hole. 